Lubricator pump



C. H. CLAUSEN LUBRICATOR PUMP Mar ch 6, 1934.

Filed April 17, 1930 7 Sheets-Sheet 1 3n we n10 r CarlHerman ('Zausen flHOrney March 6, 1934. c, H CLAUSEN 1,949,992

LUBRI CAT OR PUMP Filed April 17, 1930 7 Sheets-Sheet 2 @mmnlon Garb uevmawlausew W W Allamm;

March 6, 1934. c, c s 1,949,992

- LUBRICATOR rum? Filed April 17, 1930 '7 Sheets-Sheet 3 Fig. 5

4 01 J a 4 f March 6, 1934. c cLAUSEN 1,949,992

LUBRI CATOR PUMP Filed Agfil 17, 1930 7 Sheets-Sheet 4 TinuenLor (1% llermonc lduseru March 6, 1934. c. H. CLAUSEN 1,949,992

LUBRICATOR PUMP Filed April 17, 1930 7 Sheets-Sheet 6 9 P I Fig.3

I3 nve nto r Carl Herman Clausen March 6, 1934.

c. H. CLAUSEN 1,949,992

LUBRICATOR PUMP 7 Sheets-Sheet 7 Filed April 17, 1930 Carl Herman Cluusen Patented Mar. 6, 1934 LUBRICATOR PUMP Carl Herman Clausen, Stockholm, Sweden Application April 17, 1930, Serial No. 445,104

' In Sweden April 29, 1929 6 Claims.

This invention relates to lubricating pumps for use in high pressure lubrication and which are required to deliver oil in accurate amounts, which are controllable as to quantity, and such I delivery must be consistently at high pressure. Delivery is required to be made to several points periodically and the pumps must operate with equal accuracy and consistency for either forward or reverse running of the machine or engine on which the grouped battery of pumps is being used.

It is known to arrange the battery or group of pumps in rows or in circular form. The object of the invention is to provide an improved lubricating apparatus having several technical advantages which are not present in the row or the group pump batteries in circular arrangement hitherto known. Theoretically the present invention enables the effective service of any number of lubricating points and these points are consistently served with accurate quantities at high pressure. In the lubricating pump battery herein described, the separate pumps of the battery are operated successively one after the other: each individual pump has its separate outlet and inlet for oil regulated by a control member arranged co-axially with the pump plunger and the delivery in each individual pump of the battery may be separately regulated from nil to a fixed maximum. The space required by the improved pump battery is small and it may be efiectively used with even the smallest engines. The suction and delivery strokes of each pump in the battery are eifected when the control members have brought the suction and delivery ports into full register with the suction chamber and the discharge pipe respectively and this result is obtained in spite of the fact that the control members of all the pumps of the battery are operated by a single .excentric driving member. This single excentric driving member is mounted on a central driving spindle and is operative on excentrics on the control members. The power required to drive both the pump plungers and the control members is small and is derived from the central spindle which projects at both ends of the pump body part containing the several bores of the pumps. At one end of the said pump body, there is arranged the single driving cam for the pump plungers, which project from the body at that end and at the other end of the said pump body part there is arranged the excentric driving member on the central spindle which operates on the separate excentrics on the control members, which project from the pump body at the opposite end to that from which the pump plungers project.

A feature of the improved pump also resides in its adaptability, as it may be used with equal facility for either direction of rotation. The 315 drive for the battery of pumps may thus be made of standardized design and applied to any machine without regard to the direction of rotation. A further feature consists in the slow rotation of the control members during the times 85 when the discharge and suction ports are open, and during which the full discharge and suction strokes are completed, so that the liquid is ac curately and adequately drawn in and discharged without slip by the pump plungers in their strokes.

The invention resides in the novel arrangement and combination of parts as herein more particularly described with reference to the accompanying drawings and as pointed out in the claims. In the drawings:-

Figure l is a vertical axial section through a lubricating apparatus in accordance with this invention, this section being taken in a plane between two successive control members with their co-axial plungers.

Figure 2 is a section on the line CD of Figure 1.

Figure 3 is a section on the line A.B of Figure 4.

Figure 4 is a plan view of the apparatus, the cover and an intermediate driving member of the apparatus being removed.

Figure 5 is a section to a larger scale on the line 5-5 of Figure 6.

Figure 6 is a section on the line 6-6 of Figure 5, irrelevant parts being omitted.

Figure 7 is a section on the line 7-7 of Figure 8 and-shows a modification of the operating mechanism for the control members.

Figure 8 is a section on the line 8-8 of Figure '7.

Figures 9 and 10 are views corresponding to Figs. '7 and 8 showing a modified form, Figure 9 being a section on the line 9-9 of Figure 10 100 and Figure 10 being a section on the line 10l0 of Figure 9.

Figures 11, 12 and 13 illustrate a fourth form of operating mechanism, Figure 11 being a section on the line 11-11 of Figure 12, Figure 12 a 1 section on the line 12-42 of Fig. 1 and Figure 13 a section on the line 13-43 of Figure 11.

Figures 14, 15 and 16 are views similar to Figs. 11-13 and show a fifth modification of the opcrating mechanism for the control members, Fig- 11 members f and ,f".

ure 14 being a section on the line 14-14 of Figure 15 and Figure 15 a section on the line 15-15 of Figure 14 whilst Figure 16 is a section on the line 16-16 of Figure 15.

Figure 17 is a detail showing in elevation the floating ring of Figs. 14-16.

Figure 18 is a plan of the floating ring.

Figure 19 is a section on the line 1.9-19 of Figure 3. V

Figure 20 is a diagrammatic development of the single driving cam for efiecting successively the reciprocating movements of the pump plungers or pistons.

Throughout all the various modifications, the same reference letters are employed to indicate parts performing the same or analogous functions, although the actual form of these parts varies in each modification. In Figures 1-4 the details of the operating mechanism for oscillating the control members have been omitted. In all the examples chosen for illustration there are six separate pumps in the battery each serving a different lubricating point.

The pump body part a is penetrated by six cylindrical bores (1 the axes of which are arranged in a circle about the central axis H and are all parallel thereto, see Figs. 1 and 3. There is a central driving spindle g which projects from each end of the pump body part a and at its top projection is mounted the driving cam L for reciprocating the pump plungers e successively and in a specially timed manner as hereinafter described. Where the central driving spindle g projects at the other, end of the body part a it carries the driving excentric h for the control members ,7. The delivery points for the lubricant under pressure are indicated by the reference letter 22 (Fig. 1) and of course there is a separate delivery. for each pump of the battery, The common suction or supply pipe 0 (Fig. 4) opens into bores d (Fig. 1) which lead to an annular suction chamber (1 formed by a reduced part 9 (Fig. 19) of the central driving shaft g and its bore in the pumpbody a. Each pump plunger e moves in the direction of the arrow as to suck oil from the same suction chamber d through the corresponding port 01 (Fig. 3) of which there is one for each pump, when the control member I which is arranged co-axially with the piston e in the same bore, is in the angular position in which the axial slit or port I therein is in register with the port 01 (Fig. 19). When, under the action of the driving cam L, the diametrically opposite plunger e in the circle of pumps moves in the opposite direction, oil is forced out through the discharge opening I? and the corresponding control member 7" is then in the angular position to bring the slit f into register with the port b in the pump cylinder wall and leading to the discharge'pipe 12 In Fig. 19, only two control members f and 3 arranged diametrically opposite are illustrated. All the other control members have, at any given moment, positions which vary from those illustrated in Fig. 19 in accordance with their positions in the circle of pumps in relation to the control The means by which the oscillating movements of the control members I and f" etc. are effected are described later in T various forms with reference to Figs. 5-18.

The main drive for the battery of pumps is effected through the worm gear G which drives the central spindle g, the upper projecting end g of which carries the cam L for operating the from nil to the full amount of the risef of the cam L.

A variety of mechanisms in accordance with this invention may be devised to impart the required' periodic and properly timed movements to the control members ,7. 'In all the forms herein illustrated the slits f and f are set at to one another, so that the required oscillatory movement of the control members 7 consists of a movement through 90. The driving member 'for this movement in each case hereafter described comprises an excentric on the central driving spindle g and this driving excentric imparts to crank members in the form of excentries on the control members an oscillation which is in the nature of asimpleharmonic movement, so that there is slower movement at the ends of the swing than in the centre part. As can be seen in Figure 19, the slits f and f are slightly narrower than the ports d and b. In consequence of this there is a material time when the slits f and f are in full register with the ports. It is during this material time that the pump plungers come under the action of the rises in the cam L which efiect the suction and discharge strokes. Thus although both the driving means for the pump plungers and the means for operating the separate control members are common to all the pumps of the battery, the required ideal conditions are obtained for each pump so that there is no slip or wiredrawing and the required accurate amount of oil is delivered with the full pressure. centralspindle g may act directly on the excentries on the control members f as in the forms described hereafter with reference to Figs. 5-6 and '7-8 or through intermediate members in the nature of floating members whose movements are constrained as in the remaining modifications hereafter described. In order to obtain an oscillating movement of 90 for the control members, it is necessary that there should be a definite relation between the amount-oi the eccentricity of the excentric. on the central spin.- dle g and the excentrics on the control members i as hereafter more fully explained. f

According to the form of operating mechanism for the control members i as shown in Figs. 5 w

and 6, a driving disc h is keyed on the bottom reduced diameter g of the central driving spindle y where it projects beyond the pump body a.

The disc It has a circular recess or groove h the axis H of which is out of centre in relation to the axis H of the central spindle g by an excentricity which is marked 6. Each of the control members 1, where it projects beyond'the pump body a is provided with an ex'centric i I the axis F of which has an-excentricity E in relation to the axis F of the control member itself. The relation between the excentricities is approximately I The parts f and f are rigidly fixed together or Cut The driving excentric member on the corresponding to the position of excentric axis H nearly to its extreme left position, the two control members marked f and f assume the position shown in Fig. 19. The discharge port f of the control member ,1" is then in register with the corresponding outlet b and the suction port I of the other control member f" is in register with the suction port d The other control memhers I, at the momentary position described, have their suction and discharge ports in various relations which will be substantially the harmonic displacement corresponding to their angular position in the circle of pumps in relation to the control members f and f. From this the corresponding positions of the remaining excentrics f can be readily determined geometrically. As soon as the line 2) joining the axes of the control members in the position shown in Fig. 6, crosses the line marked 55 in the rotation of the driving member h, the cylindrical surface h of the groove h presses on the excentric of the control member f and forces the same from its extreme left position to commence its gradually accelerating movement towards the right. As the rotation of the driving member it continues, the maximum acceleration of the swinging movement of the excentric f is reached when the driving disc has rotated through 90 from the position shown in Fig. 6, whereupon, as will be readily understood, deceleration sets in till the axis F takes up its extreme right position in relation to the axis F in the case of the control member I in Fig. 6. During the return swing from right to left of the control member in Fig. 6, the excenric cylindrical surface k becomes the operative surface, whilst the excentric cylindrical surface It exercises a constrainin influence to fully and accurately determine the position of the eccentric f in relation to the control member f and its position within its bore. The arrow 3/ indicates the direction of swing of the control member 1" whilst at the same time the excentric f belonging to the control member f" rotates in a reverse direction as indicated by the arrow 1/ The corresponding directions of rotation are introduced into Fig. 19. The rotation of the excentric f corresponding to the control member 1" is effected by the inner cylindrical wall b which bears on that excentric. It will be seen that lever arms are constituted corresponding in length to the radial distance between the bearing points P and P and the axes F of the members and I respectively. Whilst these rotary movements are taking place in the case of the control members f, the cam disc L, see Fig. 20, acting through the yoke pieces (2 and the adjusting screws e impart a downward movement to the left hand pump plunger c, Fig. 3, so that the said plunger completes its discharge stroke and the right hand plunger 2 simultaneously completes its suction stroke during the time the slits f and f are in full or substantially full register with their corresponding ports in the pump bores. When in the movement of the cam disc L, the screws e traverse the horizontal sections 8 and e (see Fig. 20) of the cam L, the reciprocating movement of the corresponding pump plunger is arrested for a time corresponding to the length of these horizontal sections. It is the sloping parts of the cam L between the horizontal sections e and e which efiect the actual movement of the pump plungers and these slopes in the cam L are operative when the control members f and ,f" are in the positions shown in Figs. 19 and 6.

One cylindrical wall k operates to press and rotate one group of excentrics 1 whilst the other cylindrical surface 7L against which these same excentrics bear exercises a constraint on the movement of the control members 1 to prevent them from overshooting or moving beyond their correct positions. By the co-action of the walls It and h on'one and the same excentric F, the accurate timing and location of all the control members 1 are assured. It will be understood that the detailed description herein given in respect of the control members f and 1 applies in turn to all the other control members when the cam L and the driving disc h are rotating.

In the form according to Figures 7 and 8, the excentric groove h is formed by the loose ring 2' which rests on the disc h and this disc is in turn fixed in the same manner as described with reference to the form shown in Figs. 5 and 6. The method of operation is also in all respects similar.

In the form shown in Figures 9 and 10, a loose driving disc is is engaged by an excentric g on the central spindle g and is provided with slots k which embrace the excentrics f on the control members f. A supporting plate 1" loosely mounted by means of its hub r on the excentric g prevents the control members 7 and excentrics from axial displacement. In order to constrain the excentrics f and the control members to follow the desired movements, these excentrics f operate in circular recesses s formed in the pump body a.

When the excentric g makes a full revolution in the direction of the arrow 1/, Fig. 10, the member f oscillates to and fro through an angle of about 90, the two end positions of the excentric radius 6' being shown in the case of the control members marked ,2" and ,f. The directions of these oscillations are indicated by the arrows 1/ and 111 During this oscillation the excentric f comes once in contact with the circular depression s at the point P Fig. 10, whereby the correct position of the control members f and the intermediate constraining disc 7: is maintained. The same applies to all the other control members, so that when there are six pumps in the battery there are six times when a correction of the positions takes place in each revolution.

In the form shown in Figures 11-13, the crank discs or excentrics f engage in open slots k in the intermediate disc member 10 which engages loosely on the excentric g fixed on the central spindle g. The necessary constraint is applied to the intermediate member is in this case by means of a second floating or guiding member m having four large slots m, Fig. 12, freely surrounding four of the members 1 and two slots m arranged diametrically opposite one another and fitting closely around the control members marked and I. There are also two feathers or splines m which are arranged at right angles to the grooves m and. engage in slots k on the intermediate member k. By means of the parts described the required constraint is placed on the movement of the intermediate member is which in turn acts on the excentric discs f on the control members 1. It will be noted that the guide member m only can reciprocate in the direction of the arrows r Fig. 12, Whilst the intermediate member is only can reciprocate in a direction at right angles thereto. By the action of these two constrained floating discs, it will be readily understood that the control members I are successively made to operate with the same timing as described above with reference to Figs. 5, 6, 19

and 20.

In the form showh'in Figs 14*18 a similar arrangement is employed to that shown in Figs. 11-13. In this case however, there is a floating ring n which, by means of projections 11. engaging in grooves 10 of the intermediate member 70, provides the required abutment to constrain the 7 intermediate member is, when operated by the excentric g to oscillate the crank discs or excentrics f through the required angle. The floating ring 12 is also restrained by further projections n at right angles to the first mentioned projections 12 and arranged on the opposite side of the ring n to engage in grooves a formed in the pump body a. The operation of this device is analogous to the device described with reference to Figs. 11-13.

To enable the herein described lubricating apparatus to be used with equal facility on machines operating with either direction of rotation or on a machine which is adapted to reverse, the driving intermediate driving member consists of a ring or boss (1 keyed on the shaft part g and this boss has a projection or snug q which engages on one or other side of an arcuate projection L on the cam disc L. If the snug q is on one'side oi the arcuate projection L all the pumps of the battery work correctl for one direction of rotation of the spindle g. If the direction of rotation is reversed, all the plungers c remain at rest until the projection orv snug q comes into contact with the other side I of the arcuate projection L viz the side L when the plungers e are again set in motion and operate in correct timed relation to the control members f. These members f have of course in the meanwhile, been operated by any of the mechanisms herein described and thus the relative rearrangement of the parts is obtained to enable correct and accurate working in either direction of rotation.

I claim:

' 1. In a pressure lubricatingdevice having a plurality of pumps arranged in a single'pump body and disposed in a circle about a central driving spindle, driving means common to all said pumps and located at one end or said body, separate control members for each pump and arranged to oscillate about an axis cc-axial with the pump, said control members projecting from said body at the end opposite to said pump driving means, discs excentrically arranged with respect to said control members and carried by said members externally of the pump body, an eccentrically grooved disc mounted on said central driving spindle and engagin said excentrically mounted iscs on the control members, substantially as described.

2. Means for controllingthe inlet anddischarge of each member of a battery of pumps arranged in a circle in a pump body and operated successively' by a central drivingspindle comprising, oscillatory control members mounted co-axially with said pumps, excentrics on said control members external to said pump body, an excentric on iting and constraining the said angular movement of the control members to the extent and phase of said angle as determined by the excentric on the driving spindle, substantially as described.

3. Means for controlling the inlet and outlet of each member of a battery of pumps arranged in a circle in a pump body and operated successively by 'a'centr al driving spindle comprising, oscillatory control members mounted co-axially with said pumps, excentrics on said control members external to said pump body, an excentric on said central driving spindle and operative on said excentrics on the control members and a loose ring embracing all the excentrics on the control members, substantially as described.

a. Means for controlling the inlet and discharge of each member of a battery of plunger pumps arranged in a circle in a pump body and operated successively from a central driving spindle comprising, oscillatory control members mounted co-axially with and in the same bores as the pump plungers, 'excentrics on said control members, an excentric on said driving spindle and operative on the excentrics on said control members, means for constraining the angular movements of the control members to the extent and phase of the excentric on the driving spindle and a single camon the driving spindle for operating said pump plungers to make each plunger complete its suction stroke whilst the co-axial control member isat one end of its oscillatory movement and then to complete its discharge stroke whilst said control member is at the other end or" its oscillatory movement.

5. A pressure lubricating device comprising a pump bodyhaving a plurality of bores arranged in a circle, pump plungers and separate control members arranged in said cores and projecting at opposite ends of said pump body, the control members having inlet and outlet ports, a driving spindle having its axis arranged in the centre of the said circle, a cam on and operated by said driving spindle and arranged at one end of the bores to impart a reciprocating movement successively to said pump plungers, excentrics on said control members where they project from the pump body and driving means for said excentrics and mounted on the driving spindle to impart an oscillating movement to said control members, substantially as described.

6. A pressure lubricating device comprising a pump body having a plurality of bores arranged in a circle, a driving spindle having its axis arranged in the centre of said circle, pump plungeis and separate control members arranged coaxially in said bores and projecting at opposite ends of said pump body, the control members having inlet and outlet ports adapted in the movement of said members to register alternately with inlet and outlet passages connecting to said pump bores, a cam loosely mounted on and mediately operated by said driving spindle and arranged at one end of the bores to imparu a reciprocating movement successively to said pump plungers, a coupling member rigidly secured to said driving spindle and permitting relative movement of the driving spindle towards the cam on reversal of the direction of rotation of said driving spindle, excentrics on said control members where they project from the pump body and driving means for said excentrics and mounted on the driving spindle to impart an oscillating movement to said control members, substantially as described.

CARL HERMAN CLAUSEN. 

